Single lever selectively actuated forward and reverse clutches

ABSTRACT

Clutches controlling motion in opposite directions have actuators movable oppositely, said actuators being moved by operating linkage from a control lever which includes lost motion designed to actuate one of the actuators only in one direction of lever oscillation and the other actuator in the opposite direction of lever oscillation. In a special arrangement, the driven part is locked against movement in either direction by manipulation of the normally stationary linkage to cause both disk packs to be engaged simultaneously.

United States Patent Hansen 1 1 July 1 1, 1972 [541 SINGLE LEVER SELECTIVELY 1,887,635 11/1932 Gehres et a1. ..192/48.9 x ACTUATEI) FORWARD AND REVERSE 1,338,754 5/1920 Stahl ..192/48.9 X C S 2,336,642 12/1943 Schreck ..192/21 X 2,931,476 4/1960 Zeldlel et a1. ...192/93 A X Inventor: Q Hansen. 4338 y 38, Frank- 3,138,232 6/1964 Gerber et a1. ..192/4s.9 x svllle, 53126 3,386,545 6/1968 Hansen ..192/18 R [22] Filed: Oct 12, 1970 3,386,547 6/1968 Hansen ..192/51 PP ,742 Primary Examiner-Allan D. Hermann Anomey-Wheeler, House & Wheeler [52] US. Cl ..l92/5l, 74/361, 74/471,

192/4 R, 192/18 R, 192/48.9, 192/7023, 192/93 A, 1 1 ABSTRACT 192/99 s Clutches controllin g motion 1n opposite directions have actual 21/04 Fwd 13/42 G053 9/00 tors movable oppositely, said actuators being moved by Field Of Search l R, 4 L, I}, 21, 51, operating li g f a control l which includes lost 192/93 R, 93 A, 99 S, 70.23,48.9,48.91, 7191 tion designed to actuate one of the actuators only in one direction of lever oscillation and the other actuator in the opposite direction of lever oscillation. In a special arrangement, [56] References cued the driven part is locked against movement in either direction UNITED STATES PATENTS gytanaailgulatlign oe the nongallyusltationariz linkage to cause 0 ac to enaeslmtaneous. 1,880,344 10/1932 Franco ..192/48.9 X p g g y 3,340,942 9/1967 Juhl et a1 192/51 X 6 Clainu, 12 Drawing Figures PATENTEDJUL H I972 3,675,748

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SINGLE LEVER SELECTIVELY ACTUATED FORWARD AND REVERSE CLUTCHES BACKGROUND OF INVENTION As taught in Zeidler U.S. Pat. No. 2,931,476 of Apr. 5, 1960 and in my former U.S. Pat. No. 3,386,547, it is old to operate separate clutches selectively from a single lever by providing cams which have dwells to permit motion between cam parts with which the intervening ball interacts. The instant clutch is not necessarily operated by cams but if it is so operated it is unique in that it does not and cannot depend for operation on the form of the cams. It is much simpler and less expensive to provide lost motion by simple slots in the actuating linkage.

The invention involves a combination of reversely operable clutches in which pressure is applied selectively to respective disk packs. If pressure is developed by earns, the camming mechanism may be identical in all cases, requiring no special cams and depending for selective action entirely on lost motion in the external actuating linkage. An ancillary feature involves the braking of both driven shafts by clutching them simultaneously. Since they are then engaged for rotation in opposite directions, it will be apparent that when they are clutched simultaneously neither one can rotate.

BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a view in side elevation of a drive arrangement using two oppositely rotating clutches selectively engageable by manipulation of a single lever in accordance with this in- 'vention, external linkage from the lever to the respective clutches being designed to provide lost motion to inactivate the clutch which is not in use.

FIG. 2 is a fragmentary comparable view showing a modified arrangement in which the lost motion is provided in the normally stationary portion of the linkage.

FIG. 3 is a fragmentary detail plan view of one of the clutches on the line 3-3 of FIG. 1.

FIG. 4 is a detail view of the operating lever and linkage from the viewpoint of the line 4-4 in FIG. 3.

FIG. 5 is a comparable detail view from the viewpoint of line 55 in FIG. 2.

FIG. 6 is a fragmentary detail view on an enlarged scale partially in section on the line 66 of FIG. 1.

FIG. 7 is a view taken in section on the line 77 of FIG. 6 parts being broken away.

FIG. 8 is a view in section on the line 88 of FIG. 7.

FIG. 9 is also taken in section on the line 8-8 of FIG. 7 but showing the parts in different position from that illustrated in FIG. 8.

FIG. 10 is a view somewhat similar to FIG. 1 but showing a modified embodiment of the invention which provides for braking driven shafts as well as operating in forward or reverse.

FIG. 11 is a fragmentary detail view taken on the line 77 of FIG. 10.

FIG. 12 is a fragmentary detail view taken on the line 12- 12 of FIG. 10.

DETAILED DESCRIPTION Before describing the lost motion operating means, reference is made to a simple embodiment of a drive in which motion from drive shaft 14 is communicated selectively in either direction to the driven shaft 16. A sprocket 18 on the drive shaft 14 engages a chain 20 which passes in one direction about the driven sprocket 22 of the lefthand clutch in FIG. 1 and in the opposite direction around the sprocket 24 on the righthand clutch of FIG. 1. Accordingly, the motion transmitted to the respective clutches is in opposite directions. From the respective driven sprockets 26 and 28 of respective clutches, motion is transmitted by a chain 30 to the sprocket 32 on the driven shaft 16.

The particular clutch design is also broadly immaterial to the lost motion operating mechanism herein disclosed. To emphasize this fact I have illustrated conventional clutches each of which comprises a disk pack of conventional type having interleaved outer disks 34 connected to the spider 36 (FIG. 6) upon which the driven sprocket 24 is mounted, these being interleaved with inner disks 38 connected with a hub 40 on the shaft 42 upon which the driving sprocket 24 is mounted. The arrangement as shown in FIG. 6 illustrates the righthand clutch as viewed in FIG. 1. However, the organization of the lefthand clutch is similar. Belville springs 44 may desirably be used to keep the disks of the clutch pack normally disengaged.

Engagement of the disks is effected by a pressure element 46 slidably mounted on the hub 40 and keyed thereto. Although the pressure developing means is inmaterial in a broad sense, this embodiment contemplates that the pressure plate be actuated into thrust engagement with the disk pack by means of a cam disk mounted on the other race of a thrust bearing 50 which transmits axial motion to the pressure plate 46. In the FIG. 1 construction, the disk 48 is held against rota tion by means of a link 52 mounted on a pin 54 which projects from pressure disk 48. The link is fixed against movement by a terminal ear 56 encircling the rock shaft 58 on which the control lever 60 is mounted.

At one or more places on the face of the pressure disk 48 (FIG. 6) there are cam sockets 62, preferably conical, in

which there are balls 64 also engaged in complementary cam sockets 66 in the face of the companion disk 68 of the operating pair for this clutch. The companion disk 68 may be oscillated by a reciprocable link 70 mounted on the projecting pin 72 of the disk. This pin serves as a clutch actuator to engage its respective clutch.

Having described one conventional reversible drive embodiment and one conventional set of clutches and clutch operating cams for the control thereof, 1 shall now explain the means whereby lost motion linkage enables these or other devices for like control purposes to be actuated from a single shift lever, according to the direction of movement thereof.

The link 70 is pivoted to a pin 75 on the rocker arm 59 of rock shaft 58 so that it may be reciprocated in either direction by pivotal movement of the control handle 60. However, the link 70 may have lost motion in one direction of its reciprocation respecting the driven pin 72 of the disk 68, there being a slot 76 in link 70 which, in the neutral position of the part illustrated in FIG. 1 lies at the left of the clutch actuator 72. Thus this pin will be actuated only when the link 70 is moved to the left. When the link 70 is moved to the right as viewed in FIG. I, the slotted portion of the link will pass over the pin 72 without actuation thereof.

When pin 72 is oscillated in the proper direction by oscillation of rock shaft 58, the disk 48 is oscillated angularly with respect to the paired stationary disk 48, thereby causing the ball 64 to emerge partially from both of the cavities 62 and 66 in which it is normally engaged as shown in FIG. 8. Axial yielding of disk 68 is prevented by its engagement with the stop ring 74 on shaft 42 as shown in FIG. 6. The result is to effect axial displacement of disk 48 with respect to disk 68. FIG. 8 shows the normal position of the parts when the disk pack is not compressed.

FIG. 9 shows the result of angular relative movement of disk 68 whereby disk 48 is forced to yield to the right as viewed in FIG. 6 to urge the clutch actuating pressure element 46 against the disk pack whereby motion is transmitted from the driving sprocket 48 to the driven sprocket 24 to actuate the chain 30. Assuming shaft 14 and power sprocket 18 to be rotating clockwise, sprocket 24 will likewise rotate clockwise as driven by chain 20. Thus engagement of the righthand clutch (as viewed in FIG. 1) will effect clockwise rotation of sprockets 28 and 32 and output shaft 16.

For securing counterclockwise rotation of the output shaft 16, it is necessary that the clutch which is at the right in FIG. 1 be disengaged and the clutch which is at the left in FIG. 1 be engaged. This is possible because the respective clutch actuators 72 and 720 are at opposite extremities of the lost motion slots 76 and 760.

The link 52 which engages pin 54 to hold the disk 48 stationary is also engaged with the corresponding pin 520 of the corresponding disk 480 of the clutch which appears at the left in FIG. 1. Therefore, this disk is also stationary under all circumstances.

The disk 680 which is paired with the stationary disk 480 in the lefthand clutch as viewed in FIG. 1 is provided with a pin 720 which projects through a slot 760 in the link 70. In the neutral position of the parts, this slot lies wholly at the right of the pin 720 controlled thereby. Thus when the lever 60 is actuated to shift the link 70 to the left, for the actuation of the righthand clutch, the lefthand clutch will remain inactive due to lost motion provided by the slot 760. When the lever 60 is actuated to move the link 70 to the right as viewed in FIG. 1, motion will be communicated from link thrust surface 765 to the pin 720 and thus to the disk 680 which will thereby be required to move rotatively with respect to the stationary paired disk 480. This will actuate the lefthand clutch as viewed in FIG. 1, while leaving the righthand clutch inactive. Because of the direction of movement of the chain 20 around the sprocket 22 of the lefthand clutch, the engagement of this 'clutch will result in counterclockwise rotation of sprocket 26 and sprocket 32 and output shaft 60.

It will be understood that the lefthand clutch will be actuated by axial displacement of its pressure element by axial displacement of it non-rotative disk 480 in exactly the same manner in which the pressure element of the righthand clutch in FIG. 6 is actuated by axial displacement of its stationary disk 48.

In the embodiment just described, the lost motion permitting selective operation of the respective clutches was provided by slots 76 and 670 in the link 70. Alternatively, the lost motion may be provided in the non-reciprocating link 521 which is shown in the embodiment of FIG. 2 and which is prevented from longitudinal movement by an arm 80 having an aperture closely fitted upon the rock shaft 581 as shown in FIGS. 2 and 5. The rocker arm 731 fixed to the rock shaft actuates the link 701. This corresponds to the link 70 in the FIG. 1 embodiment but has no lost motion, being pivotally connected directly with the pins 721 of the lefthand clutch and 722 of the righthand clutch. These pins are mounted on the outer disk pairs 681 and 682 of the respective clutches. In the FIG. 1 embodiment, the oscillation of the outer disk 68 of either clutch will effect axial displacement of the complementary disk 48 of that clutch due to the fact that the complementary disk is held stationary.

In the FIG. 2 embodiment axial displacement will not occur if the inner paired disk 481 or 482 is free to move. Examination of FIG. 2 will show that pin 541 of the disk 481 is at the extreme righthand end of a slot 761 in the lefthand clutch whereas the pin 542 is at the extreme lefthand end of the slot 762 in the link 521. Accordingly, when the actuating link 701 is moved to the right as viewed in FIG. 2 and thereby oscillates both of the disks 681 and 682 in a clockwise direction, the disk 481 which is paired with disk 68] will not be free to oscillate clockwise, being at the end of the slot 761. Thus relative axial displacement of these disks will be effected by the resulting ball camming action. The disk 482, on the other hand, will be free to oscillate in a clockwise direction with respect to the anchor pin 521 and therefore no camming action will occur between disk 682 and disk 482.

Opposite oscillation of the control lever 601 removes the actuating link 701 to the left as viewed in FIG. 2 to permit movement in unison of the paired disks 481 and 681 of the lefthand clutch, whereas disk 482 of the righthand clutch will not be permitted to move in a counterclockwise direction and therefore relative axial displacement of the paired disks of the righthand clutch will occur to effect engagement of that clutch.

In the construction shown in FIGS. 10 to 12, the hand lever 602 oscillates the rock shaft 582 either clockwise or counterclockwise, whereby the rocker arm 732 transmits motion from its end 752 to the actuating link 702. The slots 764 and 765 extend oppositely from the pins 724 and 725 projecting from the respective disks 684 and 685 of the left and righthand clutches. Assuming that the companion disks are held stationary as, for example, in the embodiment described in FIG. 1, it will be apparent that the lost motion provided by the slots 764 and 765 will effect operation of the righthand clutch when counterclockwise oscillation of hand lever 602 causes movement of the control link 702 to the right. Conversely, movement of control link 702 to the left will effect actuation of the lefthand clutch, while allowing the righthand clutch to remain inactive.

The anchor link 524 of this embodiment has an arm 84 held by the rock shaft 582 against lateral displacement. The pins 544 and 545, instead of being fixed in the anchor link 524 are disposed in slots 86 and 88 which extend toward each other from the respective pins. The pins are nonnally held at the remote ends of these slots by toggle members 90 and 92 which are pivotally connected to the pins and have pivotal connection centrally with a toggle actuator 94 which is connected by a yieldable link 96 with a rocker arm 98 on a rock shaft 100 operable by hand lever 102. The spring 96 is not initially under tension, being fuHy collapsed in the position of the parts shown in FIG. 10.

However, when the control lever 102 is oscillated to effect rotation of rocker arm 98, motion is communicated through the spring 96 to the toggle actuator 94 to draw the toggle links 90 and 92 upwardly at their inner ends, thereby causing the pins 544 and 545 to move toward each other in the slots 96 and 88 of the anchor link 534. This will result in simultaneous displacement of the two normally stationary disks of the respective pairs, thereby causing axial displacement thereof to engage both the lefthand and righthand clutches simultaneously, the result being to lock the transmission. The shaft 16 cannot move because each of the clutches will act as a brake for the other.

As shown in FIG. 11, the rock shaft 100 may have a projecting lug 104 selectively engageable with stops 106 or 108 in the extreme positions of the rock shaft. The lug 104 engages stop 106 only by moving over center with the spring 96 extended so that the brake will remain effective without continued pressure on the lever 102. FIGS. 10 and 11 show the lever in its two extreme positions.

I claim:

1. The combination of a driven shaft and driving connections thereto including selectively operable cam-actuated clutches each comprising a disk pack with a pin actuator, a control member selectively movable in opposed directions for engaging respective clutches, lost motion linkage connected with said member and including a link provided with slots through which said pins project, said link having at opposed ends of said slots cam surfaces for engagement with respective pins according to the direction of movement of said link and constituting means for effecting engagement of the respective clutches and thereby causing the driven shaft to be operated from respective differing clutches according to the direction of operation of said member.

2. A combination according to claim 1 in which each disk pack has a pressure plate and relatively rotatable and nonrotatable complementary cam disks, the pin actuator for each clutch being connected with the pressure plate thereof, and a complementary disk having means fixing it against rotation.

3. A combination according to claim 1 in which each clutch comprises a disk pack including a pressure plate and relatively rotatable and non-rotatable complementary camming disks, a pin actuator of each clutch being mounted on the relatively rotatable camming disk thereof and the said link provided with opposing pin-engaging surfaces having such surfaces spaced in excess of spaces between the pins of respective clutches, whereby the respective pin of one clutch may be in engagement with a pin-engaging cam surface while the respective pin of another clutch may have moved from the opposing surface according to the direction of relative movement between the pins and the link.

4. A combination according to claim 3 in which the link is relatively fixed and one pin engaged therewith is on a relatively non-rotatable cam disk.

5. A combination according to claim 1 in which a pin for operating one of said clutches is engaged with a link surface connected with a camming disk which is relatively rotatable for engagement of the respective clutch.

6. A combination according to claim 1, each of the clutches having an actuator comprising a pair of cam disks which are relatively rotatable, one disk of each pair being normally relativcly non-rotatable and the other disk of each pair being normally connected by said lost motion linkage with said member, said linkage comprising a pair of toggle links having means pivotally connecting them with each other and with which respective normally non-rotatable disks of respective pairs have lost-motion connection, a fixed anchorage with which one of the toggle links is connected, and displacing means connected with the toggle links adjacent the means 

1. TShe combination of a driven shaft and driving connections thereto including selectively operable cam-actuated clutches each comprising a disk pack with a pin actuator, a control member selectively movable in opposed directions for engaging respective clutches, lost motion linkage connected with said member and including a link provided with slots through which said pins project, said link having at opposed ends of said slots cam surfaces for engagement with respective pins according to the direction of movement of said link and constituting means for effecting engagement of the respective clutches and thereby causing the driven shaft to be operated from respective differing clutches according to the direction of operation of said member.
 2. A combination according to claim 1 in which each disk pack has a pressure plate and relatively rotatable and non-rotatable complementary cam disks, the pin actuator for each clutch being connected with the pressure plate thereof, and a complementary disk having means fixing it against rotation.
 3. A combination according to claim 1 in which each clutch comprises a disk pack including a pressure plate and relatively rotatable and non-rotatable complementary camming disks, a pin actuator of each clutch being mounted on the relatively rotatable camming disk thereof and the said link provided with opposing pin-engaging surfaces having such surfaces spaced in excess of spaces between the pins of respective clutches, whereby the respective pin of one clutch may be in engagement with a pin-engaging cam surface while the respective pin of another clutch may have moved from the opposing surface according to the direction of relative movement between the pins and the link.
 4. A combination according to claim 3 in which the link is relatively fixed and one pin engaged therewith is on a relatively non-rotatable cam disk.
 5. A combination according to claim 1 in which a pin for operating one of said clutches is engaged with a link surface connected with a camming disk which is relatively rotatable for engagement of the respective clutch.
 6. A combination according to claim 1, each of the clutches having an actuator comprising a pair of cam disks which are relatively rotatable, one disk of each pair being normally relatively non-rotatable and the other disk of each pair being normally connected by said lost motion linkage with said member, said linkage comprising a pair of toggle links having means pivotally connecting them with each other and with which respective normally non-rotatable disks of respective pairs have lost-motion connection, a fixed anchorage with which one of the toggle links is connected, and displacing means connected with the toggle links adjacent the means which pivotally connect them with each other, said displacing means constituting means for concurrently subjecting the normally fixed disks of both of said pairs concurrently to movement in a clutch-applying direction, whereby both clutches may be engaged simultaneously to lock the driven shaft. 